EP3211271B1 - Actuating arrangement and flap control system comprising the same - Google Patents

Description

The present invention relates to an actuating arrangement according to the preamble of claim 1.

Actuating arrangements of the type mentioned at the beginning are known in the prior art as electromechanical actuators and usually use a planetary gear to convert the relatively fast rotation of an output shaft of an electric motor into a slower rotation of an output element of the actuator. However, planetary gears are relatively expensive and maintenance-intensive due to their design, as they require a plurality of gears that can move on different axes. In addition, the transmission ratio (reduction ratio or gear ratio) of planetary gears is limited depending on the available installation space. Actuating arrangements that include a worm gear are also known in order to achieve a relatively high reduction ratio. However, worm gears require the bearing of two axes that are arranged at an angle to one another due to their design, which also results in increased design effort and increased installation space requirements.

The generic document DE 42 19 660 A1 discloses a method and apparatus of a mechanically driven swivel cylinder comprising steep thread pairs and one or more reduction gears.

From the FR 2 992 497 A1 an actuating arrangement with a rotating input element, a rotating output element and a gear section for converting a first torque into a second torque is known.

Also look at the documents DE 10 2007 048928 A1 , DE 10 2014 100125 A1 , WO 2014/111065 A2 and DE 10 2008 005229 referred.

The object of the present invention is to provide an actuating arrangement of the type mentioned, which converts torque with relative high transmission ratio and at the same time requires little installation space and can be produced with little design effort.

A further object of the present invention is to provide a flap control with which the movement of a flap relative to a base section can be controlled, the flap control device being inexpensive and compact.

According to a first aspect, the above-mentioned object of the invention is solved by an actuating arrangement according to claim 1.

According to an important feature of the present invention, an axially movable transmission device is provided, which is set into axial movement by the rotation of the input element, and which in turn converts this axial movement into a rotation of the output element. The first and second threaded sections of the transmission device used for this point from each other different thread pitches, through which a conversion of the torque, ie a translation or a reduction from the rotation of the input element into the rotation of the output element is achieved. The arrangement according to the invention allows, in particular, a coaxial arrangement of the axes of rotation of the input element and output element in order to simplify the bearing arrangements for the elements involved. Furthermore, the choice of different thread pitches enables the actuating arrangement according to the invention to be implemented in a simple construction and with a compact design. Depending on the design of the thread sections and the thread pitches, even very high transmission ratios can be achieved in a simple manner.

According to a preferred embodiment, it is provided that the transmission device comprises a spindle nut and that the first threaded section and the second threaded section are formed on different sections of the spindle nut, wherein preferably one of the two threaded sections forms an internal thread of the spindle nut and the other threaded section forms an external thread of the spindle nut . This embodiment enables a particularly simple structure, since in particular the two threaded sections can be formed on one and the same component, a spindle nut. In particular, a material-uniform or integral element, e.g. B. the spindle nut, can be provided as a transmission device, whereby the manufacturing costs can be further reduced and a particularly compact design can be realized.

The actuating arrangement can have a main axis around which the input element and the output element rotate and along which the transmission device can also be axially displaced. This variant not only allows the production of a particularly simple and cost-effective actuating arrangement but can also be used in the form of an elongated, in particular cylindrical, actuating arrangement. so that their design is particularly suitable for use in a flap control device for controlling the movement of a flap.

Preferably, the input element is in threaded engagement with the first threaded section of the transmission device and/or the output element is in threaded engagement with the second threaded section of the transmission device, so that a direct transmission between the respective elements reduces friction losses and contributes to a reduction in the number of necessary components. In particular, the actual transmission section can then be realized with essentially only three moving elements, the input element, the transmission device and the output element.

In a further embodiment of the present invention, the second threaded section can engage with a threaded element fixed to the housing. In further embodiments of the invention, the transmission device can be connected to the input element or to a section fixed to the housing in an axially displaceable but rotationally fixed manner. Such measures allow the axial movement of the transmission device to be decoupled from the input element and/or the output element and/or the housing.

The actuating arrangement can further have a motor arrangement by which the input element is driven in rotation. If the motor arrangement is part of the actuating arrangement, the mechanical or movable components form an easy-to-assemble structural unit which, in particular, can only be contacted electrically. There is no need for positioning and rotation-proof mounting between the motor arrangement and the input element. Alternatively, the input element of the actuating arrangement can be designed to be coupled in a rotationally fixed manner to an output shaft of a motor arrangement, so that the motor arrangement is then not part of the actuating arrangement.

If the actuating arrangement comprises the motor arrangement in one structural unit, the motor arrangement preferably has a motor and a transmission, wherein the output element of the motor is input into the transmission and an output torque of the transmission drives the input element. An additional conversion stage for the torque of the motor can thus be provided in order to achieve, for example, a particularly high transmission ratio of the entire actuating arrangement. In this case, a planetary gear transmission is particularly considered, which is then arranged in particular axially between the motor and the rotating input element.

In a further preferred embodiment of the invention, the actuating arrangement further comprises an overload control device, which is designed to interrupt a rotary coupling between the output element and the motor arrangement in an overload case in which a torque is input to the output element which exceeds a predetermined overload torque of the actuating arrangement or to reduce at least over a certain rotation angle range. The overload control in particular prevents damage to the actuating arrangement and in particular to a motor arrangement in the event of the effect of an unexpected or unintentional large torque on the output element. If, for example, the actuating arrangement is part of a flap control device for controlling and moving a flap, the overload control device can prevent damage to the actuating arrangement or the motor arrangement if a larger external force, in particular due to improper manual actuation of the flap, is applied to the flap and thus an excessive torque acts on the output element. The overload control device can be arranged to transmit torque between the input element and the motor arrangement or can be arranged in front of the input element, so that a motor arrangement can be connected to the overload control device. In this way, the motor arrangement is effectively protected against overload without requiring major design changes to the transmission section would be required.

However, the arrangement of the overload control device between the input element and the motor arrangement requires a relatively high tolerance of the overload control device, since the gear section is then arranged between the point of application of the external torque, namely the output element, and the overload control device and the overload control device must therefore already be effective at relatively small torques. This also applies to an embodiment in which the overload control device is arranged between a motor of the motor arrangement and a subsequent first gear of the motor arrangement, for example a planetary gear. In an alternative variant, the overload control device can be arranged between the output element and the input element in order to avoid the aforementioned disadvantage. In other words, the installation position of the overload control device along the power transmission chain motor, first planetary gear (if present), input element, gear section, output element, affects the output-side overload torque of the actuating arrangement in different operating states as follows: The difference between the output-side overload torque when the motor is driven and the overload torque when force is applied to the output element increases with increasing distance of the overload clutch from the output element.

In a variant of the invention, in which the overload control device in the force transmission chain described above is displaced relatively far towards the output element, it can be provided that the second threaded section engages with a threaded element, the threaded element being in normal operation, in which an output element between and motor arrangement is less than a predetermined overload torque, is held non-rotatably by the overload control device with respect to a housing of the actuating arrangement, and wherein the threaded element is in a Overload case, in which the torque occurring between the output element and the motor arrangement is equal to or greater than the predetermined overload torque, is released for rotation relative to the housing by the overload control device. Since the second threaded section is arranged in the torque transmission path of the gear section on the side of the output element, this measure shifts the overload control device towards the output element, ie towards where the excessive torque is actually input into the actuating arrangement.

In a further embodiment of the present invention, it can be provided that the overload control device has an axially movable coupling element which, in the event of an overload in which a torque occurring between the output element and the motor arrangement is equal to or greater than the predetermined overload torque, is displaced in the axial direction against a restoring force in order to interrupt a torque transmission via the coupling element. With such a movable coupling element, an interruption of a torque transmission in the event of an overload can be achieved using simple mechanical means.

According to a second aspect of the present invention, the above-mentioned inventive object is achieved by a flap control device for controlling the movement of a flap relative to a base section at a predetermined pivot angle, preferably an angle <= 180 degrees, wherein the flap control device comprises a flap holder on which a flap is provided or mountable, and an actuating arrangement according to the first aspect of the invention, wherein the flap holder is arranged on the output element, wherein the actuating arrangement has a housing in which the transmission device, the input element and a motor arrangement for rotating the input element are accommodated, and wherein the housing has mounting means for the operationally fixed mounting of the housing at the base portion.

According to the second aspect of the invention, the above-mentioned advantages of an inventive actuating arrangement of the first aspect of the invention are utilized in the application as a flap control device. Accordingly, the flap control device of the second aspect of the invention has a compact design and a simple structure and enables a relatively high transmission ratio for the controlled pivoting movement of the flap at the desired speed. The housing can be used simultaneously both as a housing and a fixed component of the actuating arrangement and also for mechanical support between the base section and the flap, i.e. for carrying the flap.

In a preferred embodiment of the invention of the second aspect, the flap control device comprises an actuating arrangement with an axially movable coupling element, as described above in relation to a variant of the first aspect of the invention. In such a device, the pivot angle of the flap can then advantageously be limited to values within a predetermined operating angle, wherein the coupling element has a toothing which can engage in an associated counter toothing of the actuating arrangement in order to block a relative rotation between the coupling element and the counter toothing, wherein in the direction of rotation of the coupling element, two adjacent engagement positions between the toothing and the counter toothing enclose an angle which is greater than the operating angle. Such a flap control device has the advantage that in the event of an overload, the coupling element disengages and the motor continues to rotate without driving the flap, but that when the flap actuation device is reset, for example when the flap is manually moved further after the blockage has been removed, the coupling element is then returned to the same relative position in relation to the other moving elements of the transmission section, in particular the transmission device and the output element, since within the operating angle of the flap only one such relative position is possible for normal operation.

Figur 1:

ein Schnittansicht einer Stellanordnung nach einem ersten nicht erfindungsgemäßen Ausführungsbeispiel der Erfindung in einer Schnittebene entlang einer Hauptachse der Stellanordnung,

Figur 2:

eine perspektivische, teilweise geschnittene Darstellung der Stellanordnung des ersten Ausführungsbeispiels,

Figur 3:

eine Schnittansicht einer Stellanordnung gemäß einem zweiten, nicht erfindungsgemäßen Ausführungsbeispiel der Erfindung in einer Schnittebene entlang einer Hauptachse der Stellanordnung,

Figur 4:

eine Schnittansicht einer Stellanordnung gemäß einem dritten nicht erfindungsgemäßen Ausführungsbeispiel der vorliegenden Erfindung in einer Schnittebene entlang einer Hauptachse der Stellanordnung und

Figur 5:

eine geschnittene perspektivische Ansicht einer Stellanordnung gemäß einem vierten Ausführungsbeispiel der Erfindung mit einer Schnittebene entlang einer Hauptachse der Stellanordnung,

Figur 6:

eine Ansicht gemäß Figur 5, jedoch ohne Gehäuse,

Figur 7:

eine perspektivische Ansicht einer Stellanordnung gemäß einem fünften Ausführungsbeispiel der vorliegenden Erfindung und

Figur 8:

eine perspektivische Ansicht eines Kupplungsrads der Stellanordnung des fünften Ausführungsbeispiels.

The present invention is explained in more detail below using preferred exemplary embodiments with reference to the accompanying drawings. Show it:

Figure 1:

a sectional view of an actuating arrangement according to a first exemplary embodiment of the invention not according to the invention in a sectional plane along a main axis of the actuating arrangement,

Figure 2:

a perspective, partially sectioned view of the actuating arrangement of the first exemplary embodiment,

Figure 3:

a sectional view of an actuating arrangement according to a second exemplary embodiment of the invention, not according to the invention, in a sectional plane along a main axis of the actuating arrangement,

Figure 4:

a sectional view of an actuating arrangement according to a third exemplary embodiment of the present invention not according to the invention in a sectional plane along a main axis of the actuating arrangement and

Figure 5:

a sectioned perspective view of an actuating arrangement according to a fourth exemplary embodiment of the invention with a sectional plane along a main axis of the actuating arrangement,

Figure 6:

a view according to Figure 5 , but without housing,

Figure 7:

a perspective view of an actuating arrangement according to a fifth embodiment of the present invention and

Figure 8:

a perspective view of a clutch wheel of the actuating arrangement of the fifth exemplary embodiment.

One in Figures 1 and 2 Generally designated 10, the actuating arrangement according to a first exemplary embodiment of the invention not according to the invention comprises a housing 12 with a fastening section 14 for attaching the actuating arrangement 10 to an external component (not shown), for example a base section or frame of a flap arrangement. A torque generated by the actuating arrangement 10 is output at an output element 16, which in the case of use in a flap control device can be attached to a flap or can be formed by a flap, so that the actuating arrangement 10 can pivot the flap relative to the base section. The output element 16 can be designed as an output lever.

Drive energy of the actuating arrangement can be provided by a motor 18, which in the exemplary embodiment is an electric motor recessed in the housing 12. An output shaft 20 of the motor 18 is preferably coupled to a gear 22 in order to achieve a first torque conversion, in particular to convert the relatively high output speed of the motor 18 into a lower speed of a gear output shaft 24. The gear 22 is preferably a planetary gear and in this way allows a coaxial transmission of the torque from the motor output shaft 22 to the gear output shaft 24 with a relatively high conversion ratio.

The motor 18 and the transmission 22 form a motor assembly in the sense of the present invention, which provides a first torque at an input element 26. The motor assembly can alternatively be formed by only a motor, i.e. without a transmission, or can use another form of transmission instead of the planetary gear transmission 22.

In the first embodiment, the input element 26 is provided with an external thread 28 and can be used in particular as a spindle which is axially fixed and rotatable about the main axis A with respect to the housing 12. The external thread 28 of the spindle 26 is in engagement with an internal thread 30 of a transmission device 32. The transmission device 32 also has an external thread 34, which in turn is in engagement with an internal thread 36 of a threaded sleeve 38 fixed to the housing. The threaded sleeve 38 is fastened in the housing 12 or is formed by the housing 12 itself.

The internal thread 30 of the transmission device 32 has a thread pitch which is different, in particular smaller in the exemplary embodiment, than a thread pitch of the external thread 34 of the transmission device 32. Accordingly, the thread pitch of the external thread 28 of the input element 26 is also different, in particular smaller, than the internal thread 36 of the threaded sleeve 38. The transmission device 32 is rotatably and axially movably guided between the input element 26 and the threaded sleeve 38. As a result, a rotary movement of the input element 26, driven by the motor arrangement 18, 22, leads to an axial movement of the transmission device 32, the positive guidance between the transmission device 32 and the threaded sleeve 38 superimposing on this axial movement a rotational movement corresponding to the thread pitch of the internal thread 36 of the threaded sleeve 38. Since the pitch of this internal thread 36 is significantly greater than the pitch of the external thread 28 of the input element 26, the transmission device 32 rotates at a speed that is significantly smaller than the speed of the input element 26.

The transmission device 32 is coupled to the output element 16 in a torque-transmitting manner in order to drive the output element 16 in rotation. Preferably, however, the coupling between the transmission device 32 and the output element 16 is designed in such a way that the axial movement component of the transmission device 32 is not transmitted to the output element 16 in order to 16 to provide a pure rotational movement, as is desired, for example, for controlling a flap. The transmission device 32 can thus be coupled to the output element 16 in a torque-transmitting but axially displaceable manner. For this purpose, an axial toothing 40 on an outer circumference of the transmission device 32 can engage with a matching axial toothing 42 on an inner circumference of the output element 16, so that the transmission device can move in the axial direction into the output element 16 or can pull out of it, but cannot rotate relative to the output element 16. In the illustrated embodiment, the output element 16 can comprise a hollow shaft 44 in which the axial toothing 42 is formed, and can further comprise an output lever 46 which is fastened to the hollow shaft 44.

The actuating arrangement 10 constructed in this way allows a relatively high speed reduction, ie a transmission section with a relatively high transmission ratio, with a simple and compact structure. Furthermore, in Figure 1 It can be seen that the internal thread 30 and the external thread 34 of the transmission device 32 can overlap in the axial direction and/or that the internal thread 36 of the threaded sleeve 38 and the external thread 28 of the input element 26 can overlap one another axially, so that along the main axis A of the actuating arrangement 10 (axis of rotation of the input element 26) the total length of the actuating arrangement 10 can be reduced. In Figure 1 It is further illustrated that the transmission element 32 can be formed from a one-piece spindle nut and can therefore be produced particularly easily and inexpensively. Furthermore, the axes of rotation of essentially all rotatable parts of the actuating arrangement 10 are preferably oriented parallel to one another and usually also coaxially. In particular, the axes of rotation of the engine output shaft 20, transmission output shaft 24, input element 26, transmission device 32 and output element 16 all lie on the main axis A of the actuating arrangement 10, thereby ensuring a stable and compact arrangement and accommodation in a substantially cylindrical housing With reference to Figure 3 A second exemplary embodiment of the present invention, which is not according to the invention, is described below. In the following, only the differences compared to the first exemplary embodiment will be discussed in more detail. Regarding the construction and functionality of all other components of the actuating arrangement, reference is expressly made to the above description of the first exemplary embodiment.

An actuating arrangement 100 of the second exemplary embodiment comprises a housing in which a motor 118 and a gear 122 are housed. The motor arrangement formed by the motor 118 and the gear 122 provides a torque for driving an input element 126, which in turn can be designed as a threaded spindle with an external thread 128. The external thread 128 of the input element 126 is in threaded engagement with an internal thread 130 of a transmission device 132. The transmission device 132 is guided in a rotationally fixed manner with respect to the housing 112 of the actuating arrangement 100, but can be moved axially. For this purpose, in particular an axial toothing 140 on an outer circumference of the transmission device 132 can be guided in an axial toothing 142 on the inner circumference of a guide sleeve 138 fixed to the housing. The guide sleeve 138 can alternatively be formed by the housing 112 if, for example, the axial toothing 142 is formed directly on an inner circumference of the housing 112.

The transmission device 132 further comprises a second thread, in particular an external thread 134, which engages with an internal thread 136 of an output element 116. The output element 116 is held rotatably with respect to the housing 112 but axially immovable.

A thread pitch of the external thread 134 of the transmission element 132 is different, in particular larger, than a thread pitch of the internal thread 130 of the transmission device 132.

During operation of the actuating arrangement 100, the motor arrangement 118, 122 generates a first torque, which is input to the input element 126 and causes the input element 126 to rotate. This rotary movement causes the transmission device 132 to move (purely) axially along the axis of rotation A of the input element 126 due to the axial guide 140, 142. The axial displacement of the transmission device 132 is finally converted into a rotary movement of the output element 116 by the threaded engagement between the external thread 134 of the transmission device 132 and the internal thread 136 of the output element 116. Due to the different thread pitches between the internal thread 130 and the external thread 134 of the transmission device 132, a certain axial displacement path of the transmission device 132 leads to a significantly smaller angle of rotation of the output element 116 or a significantly slower rotation of the output element 116.

With reference to Figure 4 A third exemplary embodiment of the present invention, which is not according to the invention, is described below. The third exemplary embodiment is based on the construction of the first exemplary embodiment ( Figures 1 and 2 ). In the following, only the differences from the first exemplary embodiment will be discussed in more detail and with regard to all components and functions of the actuating arrangement that are not described again, reference is expressly made to the description of the first exemplary embodiment.

An actuating arrangement 200 of the third exemplary embodiment comprises a motor arrangement with a motor 218 and a transmission 222 for providing a first torque which is input to an input element 226. A transmission section for converting this first torque at the input element 226 into a second torque an output element 216, as in the first exemplary embodiment, includes the input element 226, a transmission device 232, a threaded sleeve 238 and the output element 216. However, the gear section between input element 226 and output element 216 can have a different configuration. In contrast to the first exemplary embodiment, the actuating arrangement 200 of the third exemplary embodiment comprises an overload clutch 250, which is arranged between a transmission output shaft 224 of the motor arrangement 218, 222 and the input element 226 in order to act between the output element 216 and the motor arrangement 218 in the event of the action of a torque exceeding a predetermined overload torque , 222 to interrupt the torque transmission path or to allow a relative rotation between the output element 216 and the transmission output shaft 224. In this way, in the event of the action of a high external force, for example if a flap controlled by the output element 216 runs against external resistance, overloading of the motor arrangement 218, 222 is prevented.

The overload clutch 250 includes a driver wheel 252, which is connected in a rotationally fixed manner to the transmission output shaft 224 and for this purpose is either attached directly to the transmission output shaft 224 or is carried on an adapter wheel 254, which is mounted on the transmission output shaft 224. The driver wheel 252 has teeth 255 which protrude in the axial direction from an end face of the driver wheel 252. The toothing 250 of the driver wheel 252 engages in a corresponding toothing 256 of a clutch wheel 258, which is also formed in the axial direction on an end face of the clutch wheel 258 facing the driver wheel 252. The toothings 255, 256 have teeth or notches with at least one-sided oblique or round flanks, preferably V-shaped tooth flanks or notch flanks. If the teeth 255 of the driver wheel 252 and the teeth 256 of the clutch wheel 258 are in engagement with one another, a relative rotation between the driver wheel 252 and clutch wheel 258, an axial separation of the driver wheel 252 and clutch wheel 258 and thus a loosening of the toothings 255, 256 are forced by the said inclined surfaces of the toothings 255, 256 sliding against one another.

The overload clutch 250 further comprises a clutch output gear 260, which is held on a bearing 261 in a rotatable and axially immovable manner in the housing 212. The clutch gear 258 is held on the clutch output gear 260 in a rotationally fixed but axially displaceable manner. In particular, axial serrations 262 can be provided on the clutch gear 258 and on the clutch output gear 260, which engage with one another and ensure that the clutch gear 258 and the clutch output gear 260 can move relative to one another in the axial direction, but relative rotation of the two components is blocked. By means of a spring 264, which can be supported on the one hand on the clutch output gear 260 and on the other hand on the clutch gear 258, the clutch gear 258 is preferably pre-tensioned in the direction of the driver gear 252, i.e. in the direction of engagement of the gears 255, 256. The clutch output gear 260 is preferably connected to the input element 226 in a rotationally fixed manner or is formed integrally with it.

The operation of the overload clutch 250 is explained below. In normal operation, when the motor arrangement 218, 222 is driven to move the output element 216 and this rotary movement is opposed by a resistance on the part of the output element 216 that is smaller than a predetermined overload torque, the spring 264 holds the clutch wheel 258 in engagement with the driver wheel 252, so that the rotary movement of the transmission output shaft 224 is transmitted to the input element 226 via the driver wheel 252, the clutch wheel 258 and the clutch output wheel 260 and, after torque conversion, a rotary drive of the output element 216 takes place. If the output element 216 is driven by a If an external force blocks or otherwise acts between the output element 216 and the motor arrangement 218, 222 and a torque exceeding the predetermined overload torque, i.e. an overload case occurs, this external torque is input into the overload clutch 250 via the output element 216, the transmission device 232 and the input element 226 and transmitted to the clutch output gear 260 and the clutch gear 258. The difference in torque between the clutch wheel 258 and the driver wheel 254 connected to the motor arrangement 218, 222 then leads to a sliding of the inclined surfaces or curves of the gears 255, 256 and to a separation of the engagement between the clutch wheel 258 and the driver wheel 254 against the force of the spring 264. The overload clutch 250 then allows a rotation between the clutch wheel 258 and the driver wheel 252 over the teeth of the gears 255, 256, so that the torque coupling is interrupted at this point. As soon as the external torque is eliminated or is reduced to a value below the predetermined overload torque, the overload clutch 250 re-engages under the force of the spring 264 and the actuating arrangement 200 can be operated in normal mode again.

With reference to Figures 5 and 6 A fourth embodiment of the present invention is explained below. The fourth embodiment represents a modification of the third embodiment, so that only the differences compared to the third embodiment will be discussed in more detail below and otherwise explicit reference is made to the description of the third embodiment or the first embodiment.

An actuating arrangement 300 of the fourth exemplary embodiment comprises a motor arrangement with a motor 318 and a transmission 322, which provides a first torque on a transmission output shaft 324. Via a transmission section, which, as in the first and third exemplary embodiments, has an input element 326, a transmission device 332, a threaded sleeve 338 and an output element 316, this first torque is converted into a second torque on the output element 316. Here too, the transmission section can be implemented using a different design principle for converting torque.

In the fourth exemplary embodiment, the actuating arrangement 300 also has an overload clutch 350. In contrast to the third exemplary embodiment, however, in the fourth exemplary embodiment the transmission output shaft 324 is connected to the input element 326 in a rotationally fixed manner, in particular these shafts are operationally fixed to one another. In the exemplary embodiment, an adapter element 354 is attached to the transmission output shaft 324 and carries a connecting element 353, which in turn is attached to the input element 326 by means of a screw. Alternatively, the transmission output shaft 324 could be attached directly to the input element 326 or the transmission output shaft 324 could itself directly form the input element 326. The input element 326 can be supported in a rotationally fixed manner on a bearing 361 relative to the housing 312 or relative to the threaded sleeve 338.

A carrier part 370 fixed with respect to the housing 312 carries a clutch wheel 358 on an axial guide 362, so that the clutch wheel 358 is held displaceable in the axial direction relative to the carrier part 370 and thus relative to the housing 312 but is held in a rotationally fixed manner. The carrier part 370 can either be attached directly in the housing 312 or, as in the third embodiment, can be attached to the gear 322, so that it can be pushed into or removed from the housing 312 together with the motor arrangement for easy assembly.

As in particular in Figure 6 As can be seen, the clutch wheel 358 has a toothing 356 on an axially facing end face, which can be brought into engagement with a matching toothing 355 which is provided on an axially opposite end face of the Gear sleeve 338 is provided. The teeth of the gears 355, 356 therefore each protrude from their respective components 338, 358 in the axial direction and face each other. It can also be seen that the tooth flanks or notch flanks of the gears 355, 356 are bevelled or rounded, i.e. they enclose an angle to the axial axis, so that when there is a relative rotation between the clutch wheel 358 and the threaded sleeve 338, the bevelled surfaces or roundings slide against each other and the two elements are forcibly separated from each other until the tooth engagement is released. A spring 364, which is supported on the one hand on the carrier part 370 and on the other hand on the clutch wheel 358, tensions the clutch wheel 358 in the axial direction towards the threaded sleeve 338 in order to keep the gears 355, 356 in engagement with each other.

In contrast to the construction of the first and third exemplary embodiments, in the fourth exemplary embodiment the threaded sleeve 338 is not secured against rotation in the housing 312, but can rotate relative to the housing 312. During normal operation, ie when an external torque is present between the output element 316 and the motor arrangement 318, 322, which is smaller than a predetermined overload torque, the spring 364 holds the clutch wheel 358 in engagement with the threaded sleeve 338, so that the threaded sleeve 338 is rotationally fixed relative to the housing 312 is held and the operation of the actuating arrangement 300 can be carried out in a manner analogous to that described in the first exemplary embodiment. In the event of an overload, if a torque acts between the output element 316 and the motor arrangement 318, 322 which is greater than the predetermined overload torque, the excessive torque is input into the transmission device 332 via the output element 316. Transmission device 332 and input element 326 are connected to one another by threaded sleeve 338 in the manner described with respect to the first exemplary embodiment, so that a torque also acts on threaded sleeve 338 during torque conversion. In the event of an overload, the torque on the threaded sleeve 338 is large enough to allow the teeth 355, 356 to slide against one another and to displace the clutch wheel 358 in the axial direction against the force of the spring 364. Loosening the toothing engagement between the clutch wheel 358 and the threaded sleeve 338 then allows the threaded sleeve 338 to rotate relative to the housing 312 in accordance with the rotation of the transmission device 332 and thus independently of a rotation of the input element 326. The torque transmission between the output element 316 and the motor arrangement 318, 322 is therefore on canceled at this point and an introduction of excessive torque into the motor arrangement 318, 322 can be prevented. When the overload condition is no longer present, the spring 364 moves the clutch wheel 358 back into mesh with the threaded sleeve 338, so that the latter is again held in a rotationally fixed manner in the housing and normal operation is possible again.

With reference to the Figures 7 and 8 A fifth embodiment of the invention is explained below. The fifth embodiment is a modification of the fourth embodiment, so that only the differences to the fourth embodiment are discussed in more detail below and with regard to the construction and function of all other components, reference is expressly made to the above description of the fourth embodiment, if necessary in conjunction with the description of the first and third embodiments.

In the fifth exemplary embodiment, the overload clutch 450 has essentially an identical structure as in the third exemplary embodiment, although there is a difference in the shape of the teeth 455 and 456 of the clutch wheel 458 and the threaded sleeve 438, respectively. As in Figures 7 and 8 can be clearly seen, the clutch wheel has only three projections or teeth 456-1, 456-2 and 456-3, which are arranged offset from one another at an angle of 120 °. Correspondingly, three notches 455-1, 455-2 and 455-3 are arranged offset from one another at an angle of 120° on the end face of the threaded sleeve 438. Clutch wheel 458 and threaded sleeve 438 can only be used in three different versions Rotary positions are brought into engagement with one another.

The actuating arrangement 400 of the fifth exemplary embodiment achieves a particular effect in the case of an application in which the output element 416 has a regular operating angle that is less than 120°. A common application is, for example, a flap actuating arrangement in which a flap attached to the output element 416 is to be pivoted between the open position and the closed position at a pivot angle that is less than 120°, for example approximately 90°. In such an application, the overload clutch 450 has the following effect. If the output element 416 becomes blocked or the output element 416 is otherwise subjected to excessive stress during the movement of the output element 416 within the operating angle, the torque transmission in the area of the overload clutch 450 is interrupted and thus a rotation of the input element 426 is converted into a rotation of the threaded sleeve 438 via the linear displacement of the transmission device 432. The angle of rotation of the threaded sleeve 438 then corresponds to the angle of rotation that the output element 416 would rotate if it were not blocked. In an application in which the operating angle of the output element 416 is less than 120° and thus the motor arrangement can also be set up to rotate in both directions only until this operating angle is exceeded, the rotation of the motor and thus the rotation of the threaded sleeve 438 ends before the toothing 456 of the coupling wheel 458 engages in the next toothing 455 of the threaded sleeve 438. This means that in such a fault situation, after the engine has been switched off, the output element 416 can be adjusted manually, for example, until it reaches the end point of the normal operating angle, and that each tooth of the coupling wheel 458 then re-engages in exactly the same associated notch of the threaded sleeve 438 in which the tooth had engaged during normal operation of the actuating arrangement 400 until the overload occurred. This inevitably means that in particular the The transmission device is located in relation to the longitudinal axis at exactly the position where it would be if the overload had not occurred, but the actuating arrangement 400 had been moved to the respective end position in normal operation. In this way, it can be ensured that the actuating arrangement 400 can be easily returned to an operational position after an overload has been eliminated.

The above-mentioned effect of the fifth exemplary embodiment can of course also be achieved if the clutch wheel 458 has three corresponding notches or recesses instead of the teeth 456-1, 456-2, 456-3 and the matching teeth would instead be provided on the threaded sleeve 438. Furthermore, instead of three teeth or depressions on the clutch wheel 458 and on the threaded sleeve 438, more teeth and depressions or only two teeth and depressions or even just one tooth and an associated depression can be provided. What is crucial for the above-mentioned effect is that an intermediate angle between adjacent locking positions (locking rotational positions) of the clutch wheel 458 and threaded sleeve 438 is larger than an operating angle of the output element 416, for example a maximum pivot angle of a flap in the case of a flap control device.

Finally, it should be noted that in the fifth embodiment, the threaded sleeve 438 can be formed in two parts, namely it can have a first section 438-1, which carries the toothing 455, and a second section 438-2, wherein the first section 438-1 and the second section 438-2 are firmly connected to one another. Alternatively, the threaded sleeve 438 could be formed in one part, as in the third embodiment.

Claims (9)

1. Actuating arrangement (300; 400), comprising

   a. a rotating input element (326) at which a first torque of a motor arrangement (318, 322) can be input into the actuating arrangement,

   b. a rotating output element (316; 416) at which a second torque can be output from the actuating arrangement,

   c. a transmission portion for transforming the first torque into the second torque,

   wherein the transmission portion comprises a transmission apparatus with a first thread portion and a second thread portion,

   wherein the first thread portion converts a rotation of the input element into an axial movement of the transmission apparatus and the second thread portion converts an axial movement of the transmission apparatus into a rotation of the output element, and

   wherein the first thread portion and the second thread portion have thread pitches which are different from one another,

   characterised in that the transmission apparatus (332) is connected to the output element (316; 416) axially displaceably relative to one another, but rotationally conjointly.
2. Actuating arrangement (300; 400) according to Claim 1, characterised in that the transmission apparatus (323) comprises a spindle nut and that the first thread portion and the second thread portion are formed on different portions of the spindle nut, wherein preferably one of the two thread portions forms an internal thread of the spindle nut and the other thread portion forms an external thread of the spindle nut.
3. Actuating arrangement (300; 400) according to Claim 1 or Claim 2, characterised in that the actuating arrangement has a main axis (A) around which the input element (326) and the output element (316; 416) rotate and along which the transmission apparatus (332) is axially displaceable.
4. Actuating arrangement (300; 400) according to any one of the preceding claims, characterised in that the input element (326) is in threaded engagement with the first thread portion of the transmission apparatus (332) or/and that the output element is in threaded engagement with the second thread portion of the transmission apparatus.
5. Actuating arrangement (300; 400) according to any one of the preceding claims, characterised in that the transmission apparatus (332) is connected to the input element or to a portion fixed on the housing in an axially displaceable, but rotationally conjoint manner.
6. Actuating arrangement (300; 400) according to any one of the preceding claims, further characterised by a motor arrangement (318, 322) by which the input element is rotationally driven.
7. Actuating arrangement (300; 400) according to Claim 6, characterised in that the motor arrangement comprises a motor (318) and a transmission (322), preferably a planetary gearbox, wherein an output torque of the motor is input into the transmission and an output torque of the transmission drives the input element.
8. Flap control device for controlling the movement of a flap relative to a base portion at a predetermined pivot angle, preferably an angle <= 180 degrees,

   wherein the flap control device comprises a flap holder on which a flap is provided or can be mounted and an actuating arrangement (300; 400) according to any one of the preceding claims,

   wherein the flap holder is arranged on the output element (316; 416), wherein the actuating arrangement has a housing (312; 412) in which the transmission apparatus, the input element and a motor arrangement for rotational driving of the input element are accommodated, and

   wherein the housing has holder means for operationally fixed retention of the housing on the base portion.
9. Flap control device according to Claim 8, characterised in that the pivot angle of the flap is restricted to values within a predetermined operating angle, wherein the coupling element (458) has a toothing (456) which can engage in an associated mating toothing (455) of the actuating arrangement, in order to block a relative rotation between coupling element and mating toothing, wherein two adjacent engagement positions between toothing (456) and mating toothing (455) enclose, in the direction of rotation of the coupling element, an angle which is greater than the operating angle.

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